Hydraulic process of and apparatus for converting energy



H. BAUDISCH. HYDRAULIC PROCESS OF AND APPARATUS FOR CONVERTING ENERGY.

APPLICATION FILED MAY 8, I916.

Patented July 27, 1920.

5 SHEETS-SHEET I.

, 72/4 Mrs/r LEVEL H. BAUDISCH. HYDRAULIC PROCESS OF AND APPARATUS FORCONVERTING ENERGY.

APPLICATION FILED MAY 8. I 9I6.

H. BAUDISCH. HYDRAULIC PROCESS OF AND APPARATUS FOR CONVERTING ENERGYAPPLICATION FILED MAY 8, I9I6.

Patnted July 27, 1920.

5 SHEETS-SHEET 3- l/VWARD FL 0 W REACT/0N H. BAUDISCH. HYDRAULIC'PROCESSOF AND APPARATUS FOR CONVERTING ENERGY. APPLICAHON FILED MAY 8, me.

Patented July 27, 1920.

5 SHEETSSHEET 4.

H. BAUDISCH. HYDRAULIC PROCESS OF AND APPARATUS FOR CONVERTING ENERGY.

APPLICATION FILED MAY 8, I9I6.

5 SHEETS-SHEET 5.

UNITED STATES PATENT OFFICE.

HANS BAUnIsCH, or VIENNA, AUs'rRrA, AssieNoR To ALLIs-oHALMERs MANU-FACTURING COMPANY,- or MILWAUKEE, WISCONSIN, A CORPORATION OF DELAWARE.g v

.HYDRAULrc rROCEss or AND APPARATUS FOR CONVERTING ENERGY.

Specification of Letters Patent. Patented July 27, 1920.

Application filed may 8, 1916. Serial No. 96,731. '7

To all whom it may concern."

Be it known that HANS BAUDIsoH, a subject of the Emperorof Austria,residing at Vienna, Austria, has invented a certain new and usefulHydraulic Process of and Apparatus for Converting Energy, of which thefollowing is a specification.

This invention relates to a hydraulic process of and apparatus forconverting energy into another form.-

The object of the invention is to utilize a process and to produce anapparatus whereby energy will be converted into another form in such away that it is possible to secure high speeds of rotating parts. I

A clear conception of the invention maybe had by referrlng to thedrawings accompanying and forming a part of this specification in whichlike reference characters designate the same or SlIllllll? parts andvalues.

Figure 1 is a diagrammatic view graphi showing different conditions ofinlet velocity corresponding roughly to different types of turbine.

inlet velocities terminate cally determining the type of turbine from acomparison oflits inlet velocity characteristics with its dischargevelocity, in the special case where the lines representing the in thesame straight line.

Fig. 6 is a diagrammatic view generally determining the type of :turbinefrom its inlet velocity characteristics as compared with an assumeddischarge velocity.

Fig. 6 is a diagrammatic View generally determining the type of turbinefrom its discharge'velocity characteristics as compared with an assumedinlet velocity.

- less deflection than that of Fig; 7

Fig. 8 is a diagrammatic view graphically indicating the relationsbetween velocity characteristics of an axial flow turbine of the suctiontype and the relative values of the axial thrust and of the drivingforce Fig. 9 is a fragmentary sectional view of A an axial flow suctionturbine wheel indicating the nature of theflow when it cuts loose fromthe walls of the runner spaces.

Fig.10 is a diagrammatic view graphically indicating the inlet anddischarge ve locity relations and direction of flow, in radial flowreaction, limit and suction tur bines, where the discharge velocityrelative to the wheel is greater than the relative inlet velocity.(including modification for cen- 1 trifugal force) Fig. 11 is adiagrammatic view similar to Fig. 10, but where the inlet and dischargevelocities relative to the wheel are equal (ineluding modification forcentrifugal force).

Fig. 12 is a diagrammatic view similar to Figs. 10 and 11, but where thedischarge velocity relative to the wheel is smaller than the relativeinlet velocity (including modification for centrifugal force).

Fig. 13 is a fragmentary central section of a suction type of waterwheel more readily adaptable for use with swivel gates of the Fink type.

Fig. 13 is a fragmentary central section of a suction type of waterwheel of a design especially for high speeds.

Fig. 14.- is a diagrammatic View similar to Fig. 8, graphicallyindicating the velocity characteristics of an outward flow suctionturbinein which the accelerating effect of the centrifugal forcepredominates overthe decelerating effect of the inherent design ofsuction turbine.

Fig. 15 is'a diagrammatic View graphi- Cally comparing the dischargevelocities from the guide vanes (absolute inlet velocpletelyfilledis asfollows, referring to reference characters. of 1 Fig. ,1

c u cos or -c 10 cos a :g'qH' (1)- For 290 degrees, that is, assumingfor the sake ofsimplicity, vertical discharge of" water from, the runnerspaces, the above equation 1s reduced as follows:

According to the law. of sines, we obtain from the entrancev triangle 0/u :s1n (i l/sin (18Oa By combining this equationwith (1 the well known,relation is derived, c /gyH {sin 6,/sin(180 a B,)cos ,a QCZ) Thevelocity of-thewater leavingthe guid casing as calculated from equation(2) will be:

depending on whether,

which relation simplifies to 130;5 2ao for areaction (overpressure)turbine .(3p) ISO-5 2 for a limit (pressureless) turbine .(S 1S0-i3 2aofor a suction (underpressure) turbine (3 Up to the present time inturbine design,

it was not desirable to apply the relation;

appertaining especially to suction turbines,

because one; reasoned that this would only. 7

bring about an unnecessary increase in velocity, resulting in increasedfriction losses and also endangering the stability of flow on account ofthe underpressure prevailing between the guide casing and the runner.Therefore,so far, airwas always admitted between the guide casing andthe runner for condition (3 resulting 'in'the forced development of afree flow inthe runner spaces The admission ofirair; is accomplished in.

a well known manner. Whenitiis desired to ventilatewthe clearancezspaeebetweenth'e guidecasing and therunnerentrance, Fig.

2, the entrance width 6 of the runner is made larger. than the dischargewidth b, of the guide casing, to the amount of the thickness K of theinner and outer rims. )Vhen it is desired to ventilate the runner, Fig.2*, each individual runner space is ventilated-through an apertureformed in the side walls of the rim. Or ventilation may be efiectedin:the same manner asis the case the flowing stream,

If, notwithstanding the; ob]ections stated above, ventilation isprevented by sealing;

from atmosphere-the. flown in a, full gated free ,j et turbine, and adraft tubeis provided into which the :WfllJBI" discharges after leavingtherunner, then the ,air; will be. expelled from theirunner spaces sothat these. spaces willfill up, withrwater. In order to keep the runnerspaces continuously filled, it followsthat thevelocitypfthe waterleaving the guide casing is necessarily larger; than the spoutingvelocity.- Thus the, suction (underpressure) turbines, are, attained, inwhich the runner exerts a suction effect upon the guide casing,sothat-there will be a low pressure, lower than atmospheric, in theclearance space, betweenthe guide casing and the -runner.- Fronr thisitfollows at once that suction turbines can be made to benefit by theuseof draftztubes, asmuch as isI the case with limit (pressureless)turbines, and with reaction (overpressure) turbines, andthattheyareaalso adapted to discharge larger quantities. than they would ifthey acted asifreeujet. turbines, for the reason that pressure) turbine,according to, relationv (3 andtriangle-AB C the suction .(underpressure)turbine, according to. relation (3 or respectively, itscorresponds tothe.

typical action (impulse) turbine, ifwe con- 'sider thetenforceddiscontinuity of the flow lrloweverf it, may be pointed out here that.these exceedthrough; the, runner, spaces.

ingly simple relations of the angles should be considered to be onlyapproximately correct. They are not only derived from the equations ofthe classic hydraulics which in fact is itself incorrect, but they areobtained from same on the basis of fundamental simplifications. Thecharacteristics of the individual types of turbines are obtained moreaccurately, although in a somewhat more complicated manner, on the basisof the graphic representation of the turbine equations.

The first principal equation for full gated turbines with completelyfilled runner spaces is as follows:

For axial discharge turbines this equation If, in considering reaction(overpressure) turbines, we introduce the expresslon,

for the reaction velocity, and, in considering suction (underpressure)turbines, the expression 1 for the suction velocity, then, for the limitturbines we will have as a limit between the reaction (overpressure)turbines and the suction (underpressure) turbines,

c =c,=O (5 Equations (4 can then be written: For the reaction turbine, w-zu =c,p .(By) For the limit turbine, w =w ..(6 For the suction turbine,w w =ca .(6

By inserting the corresponding values of Fig. 4, we obtain the followingtabulation:

Pressure turbine.

( 3 91x32 w; 13 0 +EB 0,, EFF 1E (OE EDP) (CE EDP) (GDP) (DPDG) 0,, D Gw," w

Limit turbine.

(m +EB2 @0 (IE E3 6, DSE2 (E (DSE EC) E0) 1) 0 or (FDG) The value c, ofthe suction turbine can, therefore,be represented in a similar manner asthe value 0,, of the pressure turbine.

If we write i g( w) then We can write equations (5) as follows:

c, =c c, (8

These values are represented by means of the auxiliary points J and Kfor the pres sure turbine and the suction turbine, and distance ADrepresents the value c, for the limit turbine.

From the above it follows, Fig. 5, that each point D of the straightline gg to the left of D corresponds to a reaction (overpressure)turbine, each point D to the right of D corresponds to a suction(underpressure) turbine, while D itself represents the limit(pressureless) turbine.

This can be defined still more generally by referring to Fig. 6, whereany point D inside of the circle K represents the end point D of theentrance triangle of a reaction turbine; where each point D; upon thecircle K represents the same end point of the entrance triangle of alimit turbine; and where each point D outside of the circle K representsthe end point D of the entrance triangle of a suction turbine. On theother hand, by referring to Fig. 6", any point C inside of the circle Krepresents the end point C of the discharge triangle of a suctionturbine; any point C upon the circle K represents the same end point ofthe dis-' charge triangle of a limit turbine; and any point CF outsideofthe circle K represents the endpoint C of the discharge triangle of areaction turbine.

, veloped in the runner spaces chiefly by the acceleration of the waterflowing through the same, and the maximum deflection of the water streamlines is ofinferior importance. In the limit turbine [and of course inthe true action (impulse) turbine] the energy is developed in the runnerspaces by the deflection of the water along the concave surface of therunner blade. In the suction turbine however, the energy results fromthe deceleration of the water flowing through the runner spaces. (Thisof course, is done by progressively increasing the cross-section of therunner spaces.) Hence here, as in the case of the reaction turbine, therequirement of maximum deflection of the stream lines is of inferiorimportance. Consequently, not only a curvature of the runner blades asshown in Fig; 7, but also one as shown in Fig. 7" is perfectly feasible.It therefore follows that the suction turbine is a type in which highperipheral speeds are obtainable. I

In'every case the energy'is developed by conversion of the absolutevelocity of the water flowing through the runner, which conversionresults from the impulse (pressureexerted by water in motion which isdue to its kinetic energy) of the 'water against the leading sides ofthe runner channels, and is always a consequence of deflection. Anystatic pressure in the runner channels is mainly balanced with referenceto the rotary motion of the runner.

In the limit-turbine, and in the free jet or impulse turbine, thevelocity converted into power is derived directly from that which is dueonly to thehydrostatic head. The deflection of the stream and consequentdevelopment of power involves deceleration of its absolute velocity.

stream due toth'e hydrostatic head is enhanced as it passes through therunner, by the nozzle effect of each runner channel which diminishes insections normal to the direction of'travel of the stream from the pointofentrance to the point of exit, in comparison with what those sectionswould "be in an otherwise similar limit turbine. In thedeterminationof'the velocity of flow through a runner the flow through which has agreater or less radial-component, the centrifugal force must beconsidered and inight'even so affect the velocity as to be less at; theoutletthan at the inlet of the runner. In the reaction'turbine thereforewhere the-runner channel is progressively diminishing in' section, andassuming a given angle of deflection andamount of en ergy imparted tothe runner, the relative velocity of the stream of water passing anypoint in the runner channel is accelerated in comparison with what itwould be in the absence of the nozzle effect due to such diminution ofsection of the runner channel. But the runner abstracts more energy fromthe stream, having a greater velocity to derive energy from, than itwould with the same angle of deflection in the absence of the nozzleeffect. Thus the energy developed in a reaction turbine is chiefly dueto acceleration of the relative velocity of the stream, notwithstandingthe fact that the In the reaction turbine, the velocity of the Y energyabstracted from the stream by the runner reduces the absolute velocity,and may, on account of the effect of centrifugal force, as for instancein radial inward flow turbines, even reduce the actual relative Velocityat the point of exit in comparison with the corresponding velocity atthe point of entrance. In the suction turbine, in which each runnerchannel enlarges between the inlet and the outlet in sections normal tothe direction of the stream, and the runner channels are kept fullofwater during'the operation, the form of; each runner channel producesa deceleration of the relative velocity of the stream, that is, therelative velocity which it'has at the point of exit is less incomparison with the relative velocity which it has at the point ofentrance. The immediate effect of that deceleration is the conversion ofrelative velocity into static pressure, which can have little directeffect upon the rotation of the runner since static pressures in the'runner channelsare mainly balanced with reference to that motion. Butthis conversion produces a suction effect at the kinetic energy in thestream which may be converted into usefully applied power is increasedin comparison with the total amount of kinetic energy which may be soconverted derived from the unmodified'hydrostatic head. This result isindirectly attained by deceleration-of the relative velocity of thestream flowing through the runner.-

The showing in Fig. 5 of the velocity of a suction turbine having aforwardly vaned runner, is therefore changed to that of Fig. 8. Fromthis'it follows thattlie angle a, becomes large on account. of the smallangle Large angles a correspond to large openings between the guidevanes, therefore only a moderate width of guide casing is necessary toproduce'the desireddischarge capacity of the turbine. The suctionturbine therefore, is characterized by a much less height of guidecasing, If this is an advantage in reducing the energy required forregulation following the more rugged construction of theguidecasing, itis of the greatest advantage with very low heads and of consequentcompact construction, as in this way much can be "saved in constructionthe water flowing through the full runner spaces is made known by:

em/( sin ar Sint 1 9 If we assign a Value to the expression between thebrackets w, sin {5 w sin {5 :K,

This value results in Fig. 8 as the horizontal distance between the twopoints C and D. If AL is made equal to BM equal to gall/a then the areaof the rectangle ALMB will equal 91 11. On the other hand, if arectangular triangle is drawn with AH equal 0, as hypotenuse, and withHJ equal 0, as one of the other two sides, then AJ represents theValium/291 B, since By means of the auxiliary diagram AJzAN, and whereangle NAB= 45 degrees, we obtain in AN the diagonal of the square AONP,the area of which is again g'qH. With a correct diagram therefore, thethree points A, Q, and B are located on a straight line. v

This diagram indicates that the suction turbine is a hydraulic primemover equally as important as a reaction turbine. The efficiency of asuction turbine may possibly be less favorable, on account of the veryhigh velocity 0 of water leaving the guide casing, and also on accountof the very high relative velocity 10,. However, due to the reducedcurvature of the guide vanes and runner blades, the friction andcurvature losses will be of less importance in both directing systerns.(ofthe suction turbine) The reduced diversion permits of a shorterdevelopment of both guide vanes and runner blades, without increasingthe resistance due to the diversion. The most serious objections tothesuction turbine lie in the required relative retardation of the water inthe runner space, since the velocity to, must be reduced to w, withinthis runner space. This may lead to a cutting loose of the water fromthe walls of the spaces, whereby a main flow H, Fig. 9, may be formedwithin the runner space, of almost unreduced velocity 'w through theentire runner space, and in addition to this main flow a secondary oreddy flow N which is not only energy destroying but also prevents therelative retardation which is the very feature of the suction turbine.These objections will be dispelled at once if one considers thefeasibility of applying the principle of the suction turbine to a radialflow turbine or to turbines of mixed flow.

For the purpose of subjecting the radial flow turbine to a graphicalanalysis, (where in must be considered centrifugal force of the waterbecause of its moving from its inlet position at a certain distance fromthe axis, to its discharge position at a different distance from theaxis,) we may refrain from the usual procedure of introducing anauxiliary value into equation (4), as this would only render theprocedure less clear. Instead, the velocity 0 may be introduced, whichcorresponds to the centrifugal force, stated as Here the plus sign of 0%applies to outward flow turbines and the minus sign to inward flowturbines. As in outward flow turbines the acceleration developed fromthe centrifugal force ispositive and in inward flow turbines negative,the runner chutes in either case must have a corrective component ofcross-section increasing the same at their endsnearer the axis ordecreasing the same at their ends farther from the axis. Thus equation(4:) in the case w, w,, is transformed into:

For the reaction turbine, w -w =c icF .(13p) For the limit turbine, w w=+cp .(13 For the suction turbine, 'I1J --1,v =+c,- 1: "(13 From theabove equations it is evident that the reaction turbine can be a radialinward flow turbine, as well as an axial flow turbine, and a radialoutward flow turbine, whereas the limit and the suction turbines can beradial outward flow turbines only. This conclusion can be drawn stillbetter from Fig. 10. If the discharge triangle ABC and also in BD therelative velocity w, in length and direction are so located that point Dfalls inside of circle K (compare also Fig. 6), then we obtain the valueas DG which is normal to gg. This length DG can be taken as being'thevalue c of a limit turbine according to equation (13 according-toequation (3.3 as base (or altitude) of aTectangular triangle DG S;according to equation (13p) either as hypotenuse of-a rectangulartriangle DGP 'or as base (or altitude) of a rectangular tr1- angle DGPIn the special instance, where 0 equals 0 ,in equation (13 the distancerepresents the value up of an axial flow turbine. i

Since the value 0 appears'as the base (or altitude) .ofa rectangular.triangle accord ing to equation (12), the .hypotenuse of whichis a,afor anoutward flow turbine, and the-hypotenuse of whichisu for aninward fiow turbine, it :follows i that the entrance triangle of theturbine can-be laid out in each case as follows:

A semicircle is drawn over AB:u and point G is:located upon the-circleat-a distance 'DG cp irompoint A, then we obtain or the entranceperipheral velocity of the and consequently u u according to equationPoint A therefore, corresponds to the axial flow reactionturbine. If anormal is formedon ABat A,;t hen each point P, of that normalcorresponds to an inward flow reaction turbine, wherein for the entranceperipheral velocity of this lurbine is obtained from Incaserw :,wtheequations (13 willbecome:. 7 V

For the reaction turbine, Cp -Cp =0 .Q (14 For the limit turbine, cs=o1% For the suction turbine, QF-c =O (14 i 7 From ithe above equations itis evident 7 that the reaction turbine can here be an inward flowturbine only, the limit turbine an axial flow turbine ,only, andthe,su'ction turbine ,anoutward flow turbine only. This also followsfrom F lg. 11 which is typical inasmuch as .point D is located on'thecircle K (compare also Fig. 6). With the entrance peripheral Velocity ofa suction turbine is obtained from the other leg being PG 0,,.

The entrance peripheral velocity or" a reaction turbine is obtained withHere, in the semi-circle erected on AB, point from Gr ofFig. :10 hasbeen removed to a certain extent towardA, but with c z0, according toequation (1%), pointG coincides with A. In case w w .the equations (13)will become For the reaction turbine, w ew cy fc l. (l5p) ,Fcr the limitturbine, w w =.c (15 c For the suction turbine, w 1) c vc (155) Fromwhich it follows that the reaction turbine and the limit turbine in thiscase "can be aninward flow turbine only, that on the other'lhand, thesuction turbine in thiscase can ibe conceived as "of inward flow, pureaxial flow, as welltas of outward flow. Graphicallyshown, Fig. :12,point D will be rlocatedoutside the circle K (compare also Fig. 6 Theentrance peripheral velocity of Va corresponding'inward "flow limitturspond to an inward flow -reaction turbine; r

all points 151/ located between G and A, correspondto an lnward flowsuction turbine; and finally, all po1nts S located to 'the right of A,correspond to an outward flow suction turbine. Point A proper however,represents the axial flow suction tur- 'bine. =Here also according toequation (15 (l G can be considered as the altitude (or base) of arectangular triangle CGP be- :longing to a reaction turbine thehypotenuse of the triangle being PC G and Similarly according toequation (15 CG can be considered as the 0 of a limit turbine, oraccording toequation (15 as hypotenuse of triangle C'GS or as the base(altitude) in triangle CG S from which the suction velocity 0., ="GrScan be obtained in the first case, and cs =GS in the second case. I 7

From the las t three diagrams it can be realized that an ,extended fieldof application is possible "with the suction turbine. Vith reference to9 however, the suction turbine may have the greatest prospect when whichis complied with in all designs shown in Figs. 10 and 11, where therelative retardation typical'with the suction turbine, is surpassed 10)or at'least compensated for (Fig. ll) by acceleration due to thecentrifugal force effective because of'the waters moving to a differentdistance fromthe axis while flowing from its inlet position to itsdischarge position;

This typical relative retardation may be considered to correspond to acomponent inlet section and a larger component outlet section across theflow through the runner, and the acceleration due to centrifugal forcemaybe considered to correspond to complementary components of inlet anddischarge sections added to the first mentioned component sections, thecomplementary components being of size varying in inverse functionalrelation to the centrifugal force at the inlet and discharge, that is,the larger the force the smaller the complementary component section.Thus the typical designs to be expected with a suction turbine runnerare already fixed. They may loek like Fig. 13 or Fig. 13*. Fig. 13permits of an easier application of the swivel gate type of guide vanesas introduced by Fink. Fig. 13 has the advantage of offering theconstruction of a runner of highest speed on account of its smallentrance diameter. With the first design of runner the requirements maybe set at the outer discharge portions of the runner but not at theinner portions, so that here possibly the mentioned secondary conditionof flow (pumping action of the runner blades) may appear. This is moreeasily obviated with the runner de gn made as shown in Fig. 13'. Thequestion whether the adaptability for the use of swivel gates is of suchgreat advantage may remain open especially, if. the purpose ofapplication of the suction turbine is kept in mind.

A suction turbine with acceleration of the Water in the runner'spaces(by reason of the surpassing of the deceleration due to the in herentdesign of suction turbine by the acceleration of the predominatingcentrifugal force) is more elaborately developed in Fig. 14 similarly toFig. 8. The value SH= /2gnH seemto be obtained. \Vith SH:SH,

whereby angle HS"B:: l5, degrees, we obtain the square SLl- 'M the sideof which is v a m and consequently the values and c u cos a and c a cosm in the areas of the rectangles ABOC and SBND". With the auxiliarypoints P and I Q, the, first mentioned rectangle becomes rectangle RENTof equal area, and there- 'fore the area of the rectangle S"RTDrepresents also the value g H according to equation From this it followsthat the square first referred to and the rectangle last referred tomust be of equal area, con-' sequently the points S, V and U must belocated on a straight line. I

- From all of these investigations it can be seen that the suctionturbine greatly widens the held of utilization of water power. Its

future will not be found so much with high heads, but more so in caseswhere it is a question of commercial development of low heads. As theturbine systems already known are completely sufficient for the turningto account of larger heads, the suction turbine should be onlycautiously employed here, for one reason, because Zero pressure may soonoccur between gu de casing and runner on account of the suction eiTectat that place, which in turn would cause a cutting loose of'the suctioncolumn, or, for another reason, because of the poss1bleextraction of air1n the clearance between guide casing and runner produced by the lowpressure at that place, corrosion may be brought about the same as isthecase with limit turbines. Both conditions are of no importance with thedevelopment of low heads, and it is just in this instance also where themoderate height of the guide casing of the suction turbine will be ofimpor tance as regards cost of the, construction of its setting, Thehigher the specific speed-of a runner the better it will be adapted forlow head. plants, and it is in just this direction that the suctionturbine is adapted to supplant the reaction turbine.

Of all turbine types the suction tur-v bine possesses the highestdischarge velocity between the guide vanes If this is not sufficientlyclear from the figures thus far discussed, due to therfact that thevelocity *alues derived from same are notbased.-

:uponthe same head, it can be seen imme- "diately from Fig. whichrepresentsequation (10) and equations (8). It canbe seen that for thesame 1 H the suction turbine possesses .=a discharge velocity betweenthe guide vanes, which must always be in excess of that ofthe-otherturbine systems. This high discharge velocity between :guidevanes and the large angle a of the guide vane, permit inthe suctionturbine of employing very small entrance diameters with large quantitiesof water. A resourceful field of application of the suction-turbine willespecially be the flood water turbine as well as that utilizing thepower of the tides. It will even be called upon as a stream turbine toutilize those water powers of the streams which heretofore wereconsideredcommercially impracticable of development. If a stream cannotbe dammed up then its stream velocity can be brought'to the guide casingof a suction turbine by means of suitable Shaped feeder penstocks. Thisvelocity will be increased in the guide casing due to the suctionreaction of the runner upon the guide casing, and Will'be reduced to alow discharge velocity from the runner by'transmitting the energy to therunner. In case of absence of a dam (which really .is the essentialpoint of a stream flow development), the turbine is flooded, so that thewater passing over same can'be compelled'to play the role of increasingthe head by its suction action upon the discharge of the run ner.

Figs. 16 and 17 are pictorial illustrations of'the features of theexpanding runner channels showing them sealed from atmosphere and fullof water as they are during operation. I

It is self evident that the characteristics of a suction turbine can beapplied also to other hydraulic machines,but this'however will not befurther considered here.

It should be understood that it is notdesired 'to be limited to theexact details of the process disclosed nor to. the exact details ofconstruction shown and described, for obvious modifications will occurto a person skilled in the art.

It is claimed and desired to secure by Letters Patent,'

1. The process of translating energy contained in a stream of water toenergy of another form which consists in modifying the flow through arotor located within said stream whereby independent of the effect ofthe centrifugal force on the flow a deceleration thereof would tend tobe produced.

I 2. The process of translating energy contained in a stream of water toenergy of another form by conducting said stream to a movable membersealed from atmosphere we causing a translation of energy between saidmember and said stream by modify-ing-the flow whereby independent of theeffect of the centrifugal force on the flow a deceleration of theflowthrough said memher would tend to be produced at least as to some ofthe stream lines.

3. In a hydraulic'turbine motor, the combination of a rotor, andaconduit leading to said rotor and sealing the flow thereto fromatmosphere, said rotor having its in-- let section across the-flowsmaller than its discharge sectlon across the flow.

4. Ina hydraulic turbine motor, the combination of a rotor, and aconduit leading to said rotor-and sealing the flow :thereto fromatmosphere, said rotor having its inlet sectionacross at least some ofthe stream :linesof the flow smallerthan its discharge section acrossthe same stream-lines.

5. The process of translating energy in the rotor of a hydraulic turbinemotor which :consists in modifying the flow throughsaid rotor wherebyindependent of the effect of the centrifugal force on the flow adeceleration flow by modifying same whereby independent of the effect ofthe centrifugal force on the flow a deceleration of the flow throughsaid rotor would tend'to be produced at least as to some of itsstreamlines.

7. The process of converting energy from one form to another byconducting to a movable member a stream line flow sealed from atmosphereand abstracting therein the energy of saidjflow by modifying the fiowthrough said member whereby independent of the effect of centrifugalforce on the flow a deceleration of the flow through saidmember wouldtend to be produced at leastas to some of its stream lines.

8. The process of converting energy from one form to another bconducting to a movable membera flow of water sealed from atmosphere andabstracting therein the energy of said flow by modifying the flowthrough said member whereby independent of the effect-of centrifugalforce on the flow a deceleration of the flow through said member wouldtend to "be produced.

9. The process of converting energy from one form to another by"establishing in a conduit a flow of water and abstracting in a movablemember therein the energy of said flow by modifying the flow throughsaid member whereby independent of the effect of centrifugal force onthe flow a deceleration of the How through said member would tend to beproduced.

10. In a hydraulic'turbine motor, the coml bination of a rotor, and aconduit leading to said rotor and sealing the flow thereto fromatmosphere, said rotor having its inlet section across at least some ofthe stream lines of the flow smaller than its discharge section acrossthe same stream lines.

11. In a hydraulic turbine motor, a rotor having the flow thereto sealedfrom atmosphere and having a component inlet section across the flowtherethrough and a larger component discharge section across the floWand said rotor having complementary corrective components of inlet anddischarge section increasing the said section at their ends nearer theaxis of said rotor or decreasing the same at their ends farther from thesaid axis.

12. In a hydraulic turbine motor, the combination of a rotor and aconduit leading to said rotor and sealing the floW thereto fromatmosphere, said rotor having a component inlet section across at leastsome of the stream lines of the flow and a larger component dischargesection across the same stream lines, and complementary com ponents ofinlet and discharge sections across thesame stream lines respectivelyadded thereto of size bearing an inverse functional relation to thecentrifugal force at said inlet and discharge sections.

13. In a hydraulic turbine motor, the combination of'a rotor, and aconduit leading to said rotor and sealing the flow thereto fromatmosphere, said rotor having a component inlet section across the flowtherethrough and a larger component discharge section across the flow,and complementary components of inlet and discharge sectionsrespectively added thereto of size bearing an inverse functionalrelation to the centrifugal force at said inlet and discharge sections.

In testimony whereof, the signature of the inventor is afiixed hereto.

HANS BAUDISCH,

